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WO2013100509A1 - Système de prévention du dépassement de pression pour pompe hydraulique électronique incluse dans un système hydraulique - Google Patents

Système de prévention du dépassement de pression pour pompe hydraulique électronique incluse dans un système hydraulique Download PDF

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Publication number
WO2013100509A1
WO2013100509A1 PCT/KR2012/011352 KR2012011352W WO2013100509A1 WO 2013100509 A1 WO2013100509 A1 WO 2013100509A1 KR 2012011352 W KR2012011352 W KR 2012011352W WO 2013100509 A1 WO2013100509 A1 WO 2013100509A1
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WO
WIPO (PCT)
Prior art keywords
pressure
flow rate
command
hydraulic
stall
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/KR2012/011352
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English (en)
Korean (ko)
Inventor
정우용
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
HD Hyundai Infracore Co Ltd
Original Assignee
Doosan Infracore Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Doosan Infracore Co Ltd filed Critical Doosan Infracore Co Ltd
Priority to EP12862265.1A priority Critical patent/EP2801724B1/fr
Priority to US14/368,430 priority patent/US20150017029A1/en
Priority to JP2014549980A priority patent/JP5890040B2/ja
Priority to BR112014016103-8A priority patent/BR112014016103B1/pt
Priority to CN201280064940.6A priority patent/CN104011391B/zh
Publication of WO2013100509A1 publication Critical patent/WO2013100509A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/02—Stopping, starting, unloading or idling control
    • F04B49/03—Stopping, starting, unloading or idling control by means of valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
    • F04B17/04—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/08—Regulating by delivery pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/10—Other safety measures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/042—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in"
    • F15B11/0423—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in" by controlling pump output or bypass, other than to maintain constant speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20546—Type of pump variable capacity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20546—Type of pump variable capacity
    • F15B2211/20553—Type of pump variable capacity with pilot circuit, e.g. for controlling a swash plate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6333—Electronic controllers using input signals representing a state of the pressure source, e.g. swash plate angle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6652—Control of the pressure source, e.g. control of the swash plate angle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6654—Flow rate control

Definitions

  • the present invention relates to a pressure overshooting prevention system of an electrohydraulic pump of a hydraulic system. More particularly, the pressure overshooting is performed by controlling a pressure command to the electrohydraulic pump in a hydraulic system when the actuator can no longer operate. A pressure overshooting prevention system of an electrohydraulic pump of a hydraulic system that can be prevented.
  • the hydraulic system discharges the working oil from the electro-hydraulic pump, and the working oil is waiting at the inlet to the main control valve.
  • a plurality of spools are provided inside the main control valve, and a plurality of actuators are connected to the outside.
  • pilot pressure is generated in a flow request unit such as a joystick, a pedal, and the pilot pressure is provided to the main control valve.
  • the main control valve is opened and closed with a specific spool by the pilot pressure, and the operating oil is provided to the actuator associated with the spool by opening and closing the spool.
  • the hydraulic oil discharged from the electromagnetic hydraulic pump by operating the joystick is provided to the actuator via the main control valve, thereby operating the actuator.
  • the actuator is configured to have a piston rod in the cylinder, and the piston rod operates in a direction in which the piston is expanded or contracted by the pressure of the hydraulic oil.
  • a piston rod reaches an end point which can no longer be extended or a situation in which it can no longer be extended or retracted by large external loads.
  • Such a situation where the piston rod is subjected to physical resistance such that it can no longer operate can be defined as a stall.
  • the joystick or the pedal may be continuously operated regardless of whether the operator intends or does not intend it. Since the required flow rate is still required, the electro-hydraulic pump will continue to discharge the flow rate and provide it to the actuator, thereby raising the hydraulic pressure inside the hydraulic system to a dangerous level.
  • a safety relief device has a variable relief valve which opens when a pressure higher than the allowable pressure is set to discharge the hydraulic oil.
  • a hydraulic system including a main control valve with a center bypass line and a pressure-controlled electromagnetic hydraulic pump in the hydraulic system, and in such a hydraulic system, when the actuator is stalled, the swash plate angle of the electromagnetic hydraulic pump is lowered to the minimum flow rate.
  • variable relief valve when the variable relief valve is opened or the swash plate angle is adjusted to the minimum in the stall situation as described above, the hydraulic fluid is discharged in the electrohydraulic pump while the hydraulic pressure is reduced to a safe pressure and stabilized.
  • the pressure peak occurs momentarily. This pressure peak has a problem of weakening the durability of the hydraulic system.
  • FIG. 1 is a view for explaining a hydraulic system equipped with a pressure-controlled electromagnetic hydraulic pump.
  • the hydraulic system comprises a flow rate requesting unit 10 composed of a joystick, a pedal, and the like, an electromagnetic hydraulic pump 50 for discharging hydraulic oil, and an actuator 70 for opening and closing the spool. It is configured to include a main control valve 60 to be provided to.
  • the flow rate request unit 10 generates pilot pressure when an operator operates a joystick or a pedal, and the pilot pressure is provided to the main control valve 60.
  • the main control valve 60 is provided with a plurality of spools therein, the spool is operated by the above-described pilot pressure, passing the hydraulic oil when the spool is opened, and shuts off the flow of the hydraulic oil when the spool is closed.
  • the actuator 70 is provided with a piston rod in the cylinder and is connected to the main control valve 60 described above at the piston head side and the tail side to receive hydraulic oil.
  • the piston rod is stretched or retracted depending on which side the hydraulic oil is provided and discharged. Stall occurs when the piston rod cannot proceed any further. In other words, the actuator 70 is stalled when the piston rod cannot proceed any further.
  • Electro-hydraulic pump 50 discharges the hydraulic oil is formed.
  • the hydraulic pressure of the hydraulic fluid can be determined by the swash plate angle. For example, assuming that the shaft of the electro-hydraulic pump 50 rotates the same rotation speed, the high pressure is formed and the flow rate is increased in the direction in which the swash plate angle is laid down, and the low pressure is formed in the direction in which the swash plate angle is erected. Will be reduced. On the other hand, since the physical dynamic characteristics exist when the swash plate angle is changed, it takes time to set the desired swash plate angle.
  • Electro-hydraulic pump 50 is the swash plate angle is adjusted by the pump regulator 40, the pump regulator 40 is operated by the electromagnetic proportional control valve (30).
  • the electromagnetic proportional control valve 30 is operated by a pressure command, and the pressure command is received from the pump control unit 20.
  • the pump control unit 20 receives the pressure value of the pilot pressure formed in the flow rate request unit 10 and the swash plate angle value of the electromagnetic hydraulic pump 50 to calculate a pressure command.
  • the pressure command from the pump control unit 20 is applied to the electromagnetic proportional control valve 30 as an electric signal, the electromagnetic proportional control valve 30 operates the pump regulator 40, and the pump regulator 40 is an electromagnetic hydraulic pump.
  • the swash plate angle of 50 is adjusted to discharge the hydraulic oil flow rate corresponding to the required flow rate.
  • an allowable pressure can be set in the hydraulic system, and when a pressure higher than the allowable pressure is formed, the variable relief valve 80 is opened so that the hydraulic oil maintains the set pressure.
  • the allowable pressure set in the hydraulic system may be variable and may be set in accordance with the capacity of the hydraulic system.
  • FIG. 2 is a view for explaining the control logic of the pressure-controlled electromagnetic hydraulic pump in a conventional hydraulic system.
  • the pump control unit 20 receives the pressure value of the pilot pressure formed in the flow rate request unit 10 and the swash plate angle value of the electromagnetic hydraulic pump 50 to calculate a pressure command.
  • a pilot pressure is formed, and the pressure value of the pilot pressure can be understood as the required pressure value.
  • the flow rate command generation unit 21 may be data input by the hydraulic system manufacturer in advance. That is, a current signal corresponding to the required pressure value is generated, and the current signal becomes a flow rate command.
  • the current discharge flow rate can be known.
  • the displacement flow rate Delta Q is converted into the pressure command by the flow control unit 24.
  • the pressure command is to control the electromagnetic proportional control valve 30 as described above.
  • FIG. 3 is a diagram illustrating a mapping diagram of pressure and pressure commands in a control logic of a conventional pressure controlled electrohydraulic pump.
  • FIG. 4 is a flow rate change diagram according to a time change for explaining an example in which a peak occurs in a discharge flow rate by a conventional pressure controlled electrohydraulic pump.
  • the actuator 70 performs an operation of expanding or contracting.
  • the change in the flow rate is generated as the displacement flow rate delta Q.
  • the pressure command of the electromagnetic proportional control valve 30 rises to a time t2 at which the swash plate angle is moved to the minimum with a slope of a.
  • the pressure in the pump regulator 40 rapidly rises to a slope of b1 larger than the slope of a to form a peak p, and then descends to a slope of b2 to follow the pressure of the electromagnetic proportional control valve 30.
  • the technical problem to be achieved by the present invention is to reduce the discharge flow rate from the electro-hydraulic pump more quickly when a stall situation that does not receive the hydraulic fluid from the actuator electro-hydraulic pump of the hydraulic system to stabilize the hydraulic system Its purpose is to provide a pressure overshooting prevention system.
  • the pressure overshooting prevention system of the electrohydraulic pump of the hydraulic system for achieving the above technical problem, the flow rate discharge command (+) corresponding to the required pressure, the discharge flow rate discharged from the electromagnetic hydraulic pump 50
  • a flow rate command calculation unit 23 that calculates a displacement flow rate Delta Q by subtracting ( ⁇ );
  • a flow rate controller 24 for generating a first pressure command corresponding to the displacement flow rate Delta Q;
  • a stall determination unit 114 for determining a stall based on a first change rate of the flow rate command and a second change rate of the discharge flow rate;
  • a flow pressure generator 115 for generating a hydraulic oil pressure value corresponding to the discharge flow rate;
  • An inclination limiting unit (116) for generating a limit pressure command to limit an increase in inclination of the hydraulic oil pressure value;
  • a selection unit 117 for setting the limit pressure command as a second pressure command when the stall determination unit 114 determines that the stall is a stall;
  • a minimum pressure setting unit 120 configured to
  • the stall determination unit 114 of the pressure overshooting prevention system of the electrohydraulic pump of the hydraulic system according to the present invention may determine to be a stall when the second change rate is larger than the first change rate.
  • the limit pressure command of the pressure overshooting prevention system of the electrohydraulic pump of the hydraulic system according to the present invention is a time t4 at which the stall is judged to be greater than the first pressure command inclination a1 before the time t4 at which the stall is determined.
  • the second pressure command slope a2 after) may be small.
  • the selection unit 117 of the pressure overshooting prevention system of the electrohydraulic pump of the hydraulic system according to the present invention sets the system pressure command as the second pressure command when the stall determination unit 114 determines that the stall is released. It may be.
  • Pressure overshooting prevention system of the electrohydraulic pump of the hydraulic system according to the present invention made as described above, the swash plate angle in the electrohydraulic pump by changing the pressure command to control the electrohydraulic pump more quickly when the stall situation occurs Can be moved more quickly, thereby significantly reducing the hydraulic oil flow rate overshooting the electrohydraulic pump. That is, the durability of the hydraulic system can be improved by reducing the overshoot hydraulic fluid.
  • FIG. 1 is a view for explaining a hydraulic system equipped with a pressure-controlled electromagnetic hydraulic pump.
  • FIG. 2 is a view for explaining the control logic of the pressure-controlled electromagnetic hydraulic pump in a conventional hydraulic system.
  • FIG. 3 is a view for explaining the mapping diagram of the pressure and the pressure command in the control logic of the conventional pressure-controlled electromagnetic hydraulic pump.
  • FIG. 4 is a flow rate change diagram according to a time change for explaining an example in which a peak occurs in a discharge flow rate by a conventional pressure controlled electrohydraulic pump.
  • FIG. 5 is a view for explaining the control logic of the pressure-controlled electro-hydraulic pump in the pressure overshooting prevention system of the electro-hydraulic pump of the hydraulic system according to an embodiment of the present invention.
  • FIG. 6 is a view for explaining the maximum pressure limiting logic in the pressure overshooting prevention system of the electrohydraulic pump of the hydraulic system according to an embodiment of the present invention.
  • FIG. 7 is a flow rate change diagram according to a time change for explaining an example of preventing the peak in the discharge flow rate in the pressure overshooting prevention system of the electrohydraulic pump of the hydraulic system according to an embodiment of the present invention.
  • first and second flow rate change calculators 114 stall determination unit
  • Stall in the context of the present invention is when the piston rod reaches the end point when the piston rod is extended or contracted to the actuator 70, or when the piston rod can no longer move by an external load Means the phenomenon that the actuator 70 is stopped.
  • overshooting is performed in the electrohydraulic pump 50 for a time that is physically delayed by dynamic characteristics when the pump regulator 40 reacts to a pressure command issued from the electromagnetic proportional control valve 30. It means that the hydraulic oil is discharged.
  • 1 is a view for explaining a hydraulic system equipped with a pressure-controlled electromagnetic hydraulic pump.
  • 5 is a view for explaining the control logic of the pressure-controlled electrohydraulic pump in the pressure overshooting prevention system of the electrohydraulic pump of the hydraulic system according to an embodiment of the present invention.
  • the pump control unit 100 is operated by the control logic of the electrohydraulic pump.
  • the pump control unit 100 controls the electrohydraulic pump 50 to suit the required flow rate by adding or subtracting the required flow rate and the flow rate discharged from the electrohydraulic pump 50.
  • the above-described required flow rate is generated by the operation of the flow rate request unit 10. More specifically, when the flow rate request unit 10 is operated, the required pressure is generated, and the required pressure is determined at the rate set by the flow rate command generation unit 21. The required flow rate is to control the flow rate control unit 24 as a required flow rate command. The flow rate control unit 24 is switched to the pressure command corresponding to the flow rate control to control the electromagnetic proportional control valve 30.
  • the above-described electrohydraulic pump 50 may output a value of the swash plate angle, and the swash plate angle value may be provided to the discharge flow rate calculator 22 to calculate a flow rate currently discharged from the electro-hydraulic pump 50.
  • the flow rate command calculation unit 23 receives the flow rate command and discharge flow rate information described above. When the required command is added (+) in the flow rate command calculation unit 23 and the discharge flow rate is subtracted (-), the displacement flow rate Delta Q of how much the flow rate should be changed is calculated.
  • the displacement flow rate Delta Q is converted into the pressure command by the flow control unit 24.
  • the pressure command is to control the electromagnetic proportional control valve 30 as described above.
  • the hydraulic system according to an embodiment of the present invention further includes a minimum pressure setting unit 120 between the flow rate control unit 24 and the electromagnetic proportional control valve 30.
  • the minimum pressure setting unit 120 receives a pressure command from the maximum pressure limiting unit 110.
  • the minimum pressure setting unit 120 selects a small pressure command from among the first pressure command input from the flow rate control unit 24 and the second pressure command input from the maximum pressure limiting unit 110 described above, thereby providing an electromagnetic proportional control valve. To control (30).
  • FIG. 6 is a view for explaining the maximum pressure limiting logic in the pressure overshooting prevention system of the electrohydraulic pump of the hydraulic system according to an embodiment of the present invention.
  • the maximum pressure limiting unit 110 receives the pump discharge flow rate and the flow rate command to generate a second pressure command.
  • the second pressure command is generated by limiting the slope of the rising pump pressure command along a map of the slope limit 116 to set the maximum pressure in accordance with the current discharge flow rate.
  • the flow rate calculation unit 111 receives a flow rate command and a pump discharge flow rate value, and calculates and demands the flow rate.
  • the required flow rate will be changed according to the operation amount of the flow rate request unit 10, and there is a phenomenon in which the degree of change is suddenly changed or is gradually changed, and the degree of change is calculated by the first flow rate change calculation unit 112 to be required flow rate. Calculate the rate of change.
  • the second flow rate change calculator 113 receives the value of the pump discharge flow rate and calculates a second rate of change of the discharge flow rate actually discharged from the electromagnetic hydraulic pump 50.
  • the stall determination unit 114 compares the first change rate of the flow rate command with the second change rate of the discharge flow rate, and determines whether the stall has occurred in the actuator 70. That is, when the second change rate is larger than the first change rate, the stall state is determined.
  • the stall state is a state in which the piston rod of the actuator 70 does not move even though the driver is operating the joystick. Therefore, although the flow command exists, the flow path of the hydraulic system is blocked because the flow rate of the hydraulic oil is not received by the actuator 70.
  • the swash plate angle of the hydraulic pump 50 is in a state of rapidly decreasing. That is, it is determined that the stall state is when the change value for the difference between the flow rate command and the pump discharge flow rate is larger than the set value and the change value of the discharge flow rate of the electro-hydraulic pump 50 is smaller than the set value.
  • the pump discharge flow rate value is set by the flow pressure pressure generating unit 115 to the hydraulic oil pressure value corresponding to the current pump discharge flow rate.
  • the above-described hydraulic oil pressure value is increased to the inclination value set in the inclination limiting unit 116.
  • the selector 117 receives the limit pressure command set in the above-described inclination value and the system pressure command set in the hydraulic system, and outputs the limit pressure command when the stall determination unit 114 determines that the stall is the stall. If it is not a stall, the system pressure command is output.
  • the pressure command output from the above-described selection unit 117 is set to the above-described second pressure command.
  • the minimum pressure setting unit 120 finally outputs a small pressure command among the first pressure command provided from the flow rate control unit 24 and the second pressure command provided from the above-described selection unit 117.
  • Figure 7 is a flow rate change diagram according to the time change for explaining an example of preventing the peak in the discharge flow rate in the pressure overshooting prevention system of the electro-hydraulic pump of the hydraulic system according to an embodiment of the present invention.
  • the actuator 70 performs an operation of expanding or contracting.
  • the change in the flow rate is generated as the displacement flow rate delta Q.
  • the initial pressure command corresponds to the second pressure command from the time t4 at which the swash plate angle is changed by the first pressure command inclination a1 corresponding to the first pressure command, and the stall determination unit 114 determines that the stall is a stall.
  • the swash plate angle of the second pressure command inclination a2 is changed.
  • the second pressure command has a limited slope as compared with the first pressure command, so that the second pressure command slope a2 is formed lower than the first pressure command slope a1.
  • the 1st actual pressure curve b1 of the initial stage at the time t1 stalled will be a 1st pressure command. Following the slope a1, it is stabilized after being reduced to the second actual pressure curve b2 immediately after the change to the second pressure command slope a2.
  • the pressure overshooting prevention system can significantly lower the flow rate peak p by reducing the pressure command earlier.
  • the time t3 at which the swash plate angle of the electromagnetic hydraulic pump 50 is moved to the minimum can be advanced, and the flow rate (c) discharged while the swash plate angle is moved to the minimum can be reduced.
  • the pressure overshooting prevention system of the electrohydraulic pump of the hydraulic system according to an embodiment of the present invention, the stall by the final output of the small value of the output value of the maximum pressure limiting unit 110 and the flow control unit 24 as a pressure command This can reduce the pressure peak in the state.
  • the pressure overshooting prevention system of the electrohydraulic pump of the hydraulic system changes the pressure command to control the electrohydraulic pump 50 more quickly when a stall situation occurs. It is possible to move the swash plate angle more quickly in the electro-hydraulic pump 50, thereby significantly reducing the hydraulic oil flow rate (c) overshooting the electro-hydraulic pump (50). That is, the durability of the hydraulic system can be improved by reducing the overshoot hydraulic fluid.
  • the pressure overshooting prevention system of the electrohydraulic pump of the hydraulic system according to the present invention can quickly reduce the discharge flow rate of the electrohydraulic pump when a stall situation occurs in which the actuator cannot operate, thereby improving durability of the hydraulic system. It can be used to.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Reciprocating Pumps (AREA)
PCT/KR2012/011352 2011-12-27 2012-12-24 Système de prévention du dépassement de pression pour pompe hydraulique électronique incluse dans un système hydraulique Ceased WO2013100509A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP12862265.1A EP2801724B1 (fr) 2011-12-27 2012-12-24 Système de prévention du dépassement de pression pour pompe hydraulique électronique incluse dans un système hydraulique
US14/368,430 US20150017029A1 (en) 2011-12-27 2012-12-24 Pressure overshooting prevention system for electronic hydraulic pump in hydraulic system
JP2014549980A JP5890040B2 (ja) 2011-12-27 2012-12-24 油圧システムにおける電子油圧ポンプの圧力オーバーシュート防止システム
BR112014016103-8A BR112014016103B1 (pt) 2011-12-27 2012-12-24 Sistema de prevenção de sobrepressâo para uma bomba hidráulica eletrônica em um ststema hidráulico
CN201280064940.6A CN104011391B (zh) 2011-12-27 2012-12-24 液压系统的电子液压泵的压力过剩防止系统

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
KR10-2011-0142928 2011-12-27
KR20110142928 2011-12-27
KR1020120147434A KR101958489B1 (ko) 2011-12-27 2012-12-17 유압시스템의 전자유압펌프의 압력 오버슈팅 방지 시스템
KR10-2012-0147434 2012-12-17

Publications (1)

Publication Number Publication Date
WO2013100509A1 true WO2013100509A1 (fr) 2013-07-04

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US10008880B2 (en) 2014-06-06 2018-06-26 Bj Services, Llc Modular hybrid low emissions power for hydrocarbon extraction
CN114909280B (zh) * 2022-04-07 2024-05-17 潍柴动力股份有限公司 基于多源信息反馈优化的液压泵控制方法及系统

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JP2005265002A (ja) * 2004-03-17 2005-09-29 Kobelco Contstruction Machinery Ltd 作業機械の油圧制御回路
JP2009144505A (ja) * 2007-12-17 2009-07-02 Volvo Construction Equipment Ab 小旋回式掘削機のブーム衝撃緩和装置及びその制御方法
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EP2801724B1 (fr) 2017-03-01
BR112014016103A8 (pt) 2017-07-04
BR112014016103B1 (pt) 2021-04-27
JP2015507717A (ja) 2015-03-12
KR20130075659A (ko) 2013-07-05
EP2801724A1 (fr) 2014-11-12
BR112014016103A2 (pt) 2017-06-13
JP5890040B2 (ja) 2016-03-22
CN104011391B (zh) 2016-02-03
CN104011391A (zh) 2014-08-27
KR101958489B1 (ko) 2019-03-14
US20150017029A1 (en) 2015-01-15

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